Sheet folding device

ABSTRACT

Provided is a sheet folding device comprising a deceleration means which halts a sheet by pressing. A pressure member such as rubber is disposed upon the leading end of a rod-shaped member which is rotatably retained. A sheet is decelerated by the pressure member being applied obliquely to the sheet. The entire surface of the rubber does not make close contact with paper, and thus, a wrinkle is not formed in the paper. It is possible to ensure a stable folding location.

TECHNICAL FIELD

The present invention relates to a sheet folding device including asheet deceleration means for temporarily stopping or decelerating asheet such as printed paper along a transportation route.

BACKGROUND ART

Conventionally, a sheet folding device including a sheet transportationmeans for drawing out sheets of paper stacked on a sheet loading unitone at a time so as to transport them, a sheet stopper for preventingthe sheets transported by the sheet transportation means from traveling,and a sheet folding means for pinching and folding a bent portion of thesheet that has been prevented from traveling by the sheet stopper andpartially bent as a result, is well known (Patent Document 1).

PRIOR ART DOCUMENTS Patent Documents

[Patent Document 1] JP Hei 05-238637A

[Patent Document 2] JP Sho 60-23253A

[Patent Document 3] JP Sho 63-41377A

[Patent Document 4] U.S. Pat. No. 3,797,820A

SUMMARY OF THE INVENTION Problem To Be Solved By the Invention

Patent Document 2 discloses that a stopping member including rubber isattached rotatably along a predetermined axis, and the stopping memberis then pressed against a piece of paper using a solenoid so as to stopit. However, since the entire rubber surface adheres to the paperthrough this method, the paper moves along with the stopping member orthe paper becomes wrinkled. This cannot secure a stable foldinglocation.

Patent Document 3 and Patent Document 4 disclose that a clamp is pressedagainst a sheet perpendicularly from above so as to stop it. However,the sheet may be damaged through this method as it is strongly pressed.

The present invention aims to resolve the above problems and provide adevice for precisely folding a sheet of paper or the like at apredetermined location while reducing damage to the sheet.

Means of Solving the Problem

The present invention is a sheet folding device including sheettransportation means 11, 12, 13 and 14 for transporting a sheet S alonga predetermined route, sheet deceleration means 6 a and 6 b fordecelerating at least a part of the sheet while being transported by thesheet transportation means, folding means 11 and 13 and 11 and 14 forfolding a part of the sheet that is bent as the result of decelerationby the sheet deceleration means, and a control unit for controlling thesheet deceleration means.

The sheet deceleration means includes a guide member 62 for receivingthe sheet while being transported by the sheet transportation means; astopping member that includes a plate-like pressing member 63 having apredetermined thickness and a pressing member attachment 66 having thepressing member on an end surface facing the sheet and is rotatably heldat a predetermined fulcrum 63, wherein an edge ED1 of the pressingmember presses the sheet traveling along the guide member against theguide member; and a stopping member driving part 65 for rotating thestopping member around the fulcrum.

The stopping member is positioned at a waiting location where thepressing member does not touch the sheet or at a pressing location wherethe edge of the pressing member touches the sheet but the entire surfaceof the pressing member does not touch the sheet, the stopping membermoves from the waiting location to the pressing location by rotating inthe same direction as the traveling direction of the sheet, and returnsfrom the pressing location to the waiting location by rotating in theopposite direction to the traveling direction of the sheet, and thestopping member driving part rotates the stopping member from thewaiting location to the pressing location in compliance with aninstruction from the control unit, and the stopping member is held so asto rotate along a parallel axis to the travelling direction of thesheet, and the stopping member rotates due to a reaction to the sheetbeing pressed against the guide member by an edge of the stoppingmember.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a perspective view of a sheet folding device according to anembodiment of the present invention;

FIG. 2 is a drawing illustrating a state where an auxiliary guide memberof the sheet folding device according to the embodiment of the presentinvention is pulled out;

FIG. 3 is a perspective view of the auxiliary guide member according tothe embodiment of the present invention;

FIG. 4 is an operational schematic diagram of the auxiliary guide memberaccording to the embodiment of the present invention;

FIG. 5 is an operational schematic diagram of the auxiliary guide memberaccording to the embodiment of the present invention;

FIG. 6 is a schematic diagram of the internal structure of the sheetfolding device according to the embodiment of the present invention;

FIG. 7 is a side view illustrating a partially severed sheetdeceleration means according to the embodiment of the present invention;

FIG. 8 is a top view of the sheet deceleration means according to theembodiment of the present invention;

FIG. 9 is a partial expanded sectional view of the sheet decelerationmeans according to the embodiment of the present invention;

FIG. 10 is a side view illustrating the periphery of a stopping memberof the sheet deceleration means, according to the embodiment of thepresent invention, and a waiting location;

FIG. 11 is an operational schematic diagram of the stopping member ofthe sheet deceleration means according to the embodiment of the presentinvention;

FIG. 12 is an operational schematic diagram (comparative example) of thestopping member according to the embodiment of the present invention;

FIG. 13 is a block diagram of a control system for the device accordingto the embodiment of the present invention;

FIG. 14 is a block diagram of a control system for the sheetdeceleration means according to the embodiment of the present invention;

FIG. 15 is a schematic diagram (timing chart) of the sheet decelerationmeans according to the embodiment of the present invention;

FIG. 16 is a schematic diagram of a correction table according to theembodiment of the present invention;

FIG. 17 is a schematic diagram of a driving time setting table accordingto the embodiment of the present invention;

FIG. 18 is a flow chart of sensor selection process according to theembodiment of the present invention;

FIG. 19 is an operational schematic diagram of the device according tothe embodiment of the present invention; and

FIG. 20 is a schematic diagram explaining folding methods for a sheetusing the device according to the embodiment of the present invention.

FIG. 21 is a planar view of the sheet deceleration means according to amodification.

FIG. 22 is a front view of the sheet deceleration means according to amodification.

FIG. 23 is a right side view of the sheet deceleration means accordingto a modification.

FIG. 24 is an exploded perspective view of the sheet deceleration meansaccording to a modification.

FIG. 25 is an operational schematic diagram of the sheet decelerationmeans according to a modification.

FIG. 26 is a view showing the operation of the sheet deceleration meansaccording to a modification (table of observation results).

FIG. 27 is a view of the sheet skew.

BEST MODE FOR CARRYING OUT THE INVENTION

FIG. 1 is a perspective view of a sheet folding device according to anembodiment of the present invention. A sheet folding device 1 includes asheet stocker 2, which slants downward toward the inside of the device1, a paper ejection tray 80, which is located therebelow, and anoperation panel PAN for specifying a folding method for a sheet (paper).The paper ejection tray 80 is a sheet exit E.

As shown in FIG. 2, the back of the sheet folding device 1 isdetachable. This back is made up of an auxiliary guide member 90, whichhas a curved inner surface that receives a sheet protruding from sheetdeceleration means 6 a and 6 b described later.

The interior of the auxiliary guide member 90 is as illustrated in FIG.3. A plurality of (nine) plates is provided in the sheet travelingdirection. The shape of these plates is the same, as if the shape ismade by cutting out from those plates using half of a Koban-shapedobject (a half egg-shaped object). The angle thereof forms roughly aquarter of a circle.

The auxiliary guide member 90 receives at the cross section surfaces ofthe plates provided therewithin, a sheet protruding from the sheetdeceleration means 6 a and 6 b, as shown in FIG. 4 and FIG. 5.

By providing the auxiliary guide member 90, the sheet deceleration means6 a and 6 b may be smaller than the sheet and thus the sheet foldingdevice 1 may be downsized.

Further description will be given while referencing FIG. 6. The sheetstocker 2 is a portion for stacking foldable sheets S (standard-sizepaper in this example) and stocking them. A separating plate 3 made ofrubber or the like is provided on an end on the downside along the slopethereof. The sheets S stacked on the sheet stocker 2 are separated bythe separating plate 3 and are drawn out one by one from the top sheetS. A sliding plate 4, which guides the sheet S that has passed over theseparating plate 3, is provided in front of the sheet stocker 2. Aseparating plate 5 made of rubber or the like is provided on an end nearthe sheet stocker 2.

Other than this friction type, there is also a known air suction type. Afriction type, an air suction type, or another means may be employed asa supply means.

Reference numeral 10 denotes a feed roller, which is provided above theseparating plates 3 and 5, for rolling on and making contact with theupper surface of the sheet S that passes the separating plates 3 and 5.

Reference numeral 11 denotes a driving roller located on the downstreamof the sheet S drawn out between the separating plate 5 and the feedroller 10.

Reference numerals 12, 13 and 14 denote follower rollers, whichcircumscribe the driving roller 11 and rotate synchronously.

Reference numerals 15 and 16 denote conveying rollers, which transportthe sheet S that has passed between the driving roller 11 and thefollower roller 14 to the exit E (this continues to the paper ejectiontray 80).

The rollers 10 to 16 constitute a sheet transportation means fortransporting the sheet S along a predetermined route.

The driving roller 11 and the follower roller 13 are also a foldingmeans for folding a part of the sheet bent by the sheet decelerationmeans 6 a. The driving roller 11 and the follower roller 14 are also afolding means for folding a part of the sheet bent by the sheetdeceleration means 6 b.

Reference numeral 17 denotes a motor (sheet transportation means drivingpart) for rotary driving the driving roller 11 and the conveying roller15.

Reference numeral 18 denotes a transmission unit, which transmits thedynamic force of the motor 17. The transmission unit 18 includes apulley 18 a provided along an output shaft of the motor 17, a pulley 18b provided coaxially with the driving roller 11, a gear 18 c providedcoaxially with the feed roller 10, a gear 18 d for outer gearing withthe gear 18 c, a pulley 18 e provided coaxially with the gear 18 d, apulley 18 f and a gear 18 g provided coaxially with the conveying roller15, a gear 18 h for outer gearing with the gear 18 g, a pulley 18 iprovided coaxially with the gear 18 h, a timing belt 18 j wound aroundthe pulleys 18 a, 18 b, 18 e and 18 i, a pulley 18 k provided coaxiallywith the conveying roller 16, and a flat belt 18 n wound around thepulleys 18 f and 18 k.

Rotating the motor 17 allows simultaneous rotation of not only the feedroller 10 and the driving roller 11, but the follower rollers 12, 13 and14, which circumscribe the driving roller 11, and the conveying rollers15 and 16 as well. However, the feed roller 10 is made to intermittentlyrotate as a result of action of a clutch, which is omitted from thedrawing, provided coaxially with the feed roller. This allows the sheetsS on the sheet stocker 2 to be drawn out one by one at predeterminedtimings by the intermittently rotating feed roller 10 whileconsecutively rotating the driving roller 11 and the follower rollers12, 13 and 14.

Reference numeral 19 denotes a conveyance path for leading the sheethaving passed between the driving roller 11 and the follower roller 14to the exit E. The conveyance path 19 includes paired upper and lowerplates 19 a and 19 b that face each other in parallel and closeproximity. The lower plate 19 b is partially notched so as to expose theperipheries of the conveying rollers 15 and 16.

Reference numerals 6 a and 6 b respectively denote a sheet decelerationmeans. In FIG. 6, the sheet deceleration means 6 a and 6 b are arrangeddiagonally upward and diagonally downward, respectively, at locationsfacing the periphery of the driving roller 11. The angle between thesheet deceleration means 6 a and 6 b is approximately 90 degrees. Thesheet deceleration means 6 a and 6 b temporarily decelerate the sheet Sbeing transported by the sheet transportation means, so as to bend thesheet S. Note that ‘deceleration’ includes completely stopping the sheetS.

The upper sheet deceleration means 6 a decelerates the sheet S fedbetween the driving roller 11 and the follower roller 12. The lowersheet deceleration means 6 b decelerates the sheet S fed between thedriving roller 11 and the follower roller 13.

FIGS. 7 to 9 are the schematic diagrams of the sheet deceleration means6 a and 6 b. As the sheet deceleration means 6 a and 6 b are the same,the signs ‘a’ and ‘b’ are omitted from the following description whendifferentiation therebetween is unnecessary.

The sheet deceleration means 6 includes an upper guide plate 61 and alower guide plate 62, which face each other in parallel and closeproximity via a gap G that allows the sheet S to enter. The upper guideplate 61 and the lower guide plate 62 are formed by pressing a steelsheet etc. The gap G formed between the upper guide plate 61 and thelower guide plate 62 is approximately 1 to 3 mm, for example.

Reference numeral 63 denotes a rubber pad pressing the sheet S that hasentered the gap G onto the inner side (top side of the lower guide plate62 in this example) of the gap G along the thickness thereof. The pad 63is provided on the receiving end side of the gap G where the sheet Senters and exits, so as to control bending deformation of the sheet S inthe gap G. In FIG. 7, the right side is the traveling direction of thesheet S. When the sheet S is folded, it returns to the opposite sidefrom the traveling direction.

Reference numeral 64 denotes a pad transfer means for transferring thepad 63 between predetermined waiting and pressing locations. FIG. 7illustrates the waiting location of the pad 63. The waiting location andthe pressing location will be described in detail later.

The pad transfer means 64 includes a solenoid 65, which is deployed onthe upper guide plate 61 as a driving source, a pad fixing bar 66, whichis attached to the bottom of the pad 63, and a transmission link 67,which transmits a stretching force from the solenoid 65 to the padfixing bar 66.

As shown in FIG. 8 and FIG. 9, the pad fixing bar 66 extends along theroute orthogonal to the traveling direction of the sheet entering thegap G along the upper guide plate 61. The extending direction of the padfixing bar 66 is parallel to the end of the sheet S. A bracket 66 a isattached to the middle of the pad fixing bar 66. Paired brackets 66 bare attached on either end along the length of the pad fixing bar 66.Note that in FIG. 8, hatching of the portion of the pad fixing bar 66 isfor demonstrating the pad fixing bar 66 and is not a cross section.

While FIG. 8 and FIG. 9 show the pressing location, the entire surfaceof the pad 63 makes contact with the top surface of the sheet S or theinner surface of the lower guide plate 62. The pressing location in FIG.8 and FIG. 9 is slightly different from the pressing location describedin FIG. 11.

On the other hand, a long hole 61 a resulting from cutting out a portionfor the pad fixing bar 66 to be deployed, and brackets 61 b and 61 b,which result from bending up both ends of the long hole 61 a, are formedon the upper guide plate 61. The brackets 61 b and 61 b and the brackets66 b and 66 b are connected by pivots 68 and 68, respectively. Anextension rod 65 a for the solenoid 65 and the bracket 66 a areconnected by the transmission link 67. When the solenoid 65 is driven soas to extend, the pad fixing bar 66 rotates around the pivots 68(carries out circular movement). This moves the pad 63 between thewaiting location and the pressing location.

The brackets 61 b may be metal blocks instead of lanced claws.

A coil spring 69 is provided to the extension rod 65 a. Due to theresilience of this spring, the pad 63 is at the waiting location whenthe solenoid 65 is not being driven. When the solenoid 65 is driven, theextension rod 65 a overcomes the resilience of the spring 69 andshortens, resulting in movement of the pad 63 to the pressing location.When there is no driving current, the solenoid 65 allows the resilienceof the spring 69 to extend the extension rod 65 a, resulting in movementof the pad 63 to the waiting location.

As shown in FIG. 8, a sheet entry sensor 7 is provided on the upperguide plate 61. This sensor 7 detects the end of the sheet entering thegap G. The sheet entry sensor 7 is a reflection type photoelectricswitch, for example. Description of the waiting location and thepressing location of the pad 63 will be described while referencing FIG.10 and FIG. 11.

In the following description, the pad 63 (pressing member) and the padfixing bar 66 (pressing member attachment) are depicted collectively as‘stopping members’.

Thickness of the pad 63 is ‘a’ in FIG. 11(a). The pad 63 is provided onthe end (bottom) of the pad fixing bar 66 near the sheet S. The padfixing bar 66 is held rotatably at a fulcrum FC. The fulcrum FCcorresponds to the pivot 68.

AP denotes the point of action of the driving force of the solenoid 65,and F denotes acting force.

In FIG. 10 and FIG. 11(a), the stopping members 63 and 66 are at thewaiting location. That is, the pad 63 is not touching the sheet S.Reference numeral 61 c in FIG. 10 denotes a stopping member stopper forkeeping the stopping members 63 and 66 at the waiting location.

As shown in FIG. 11(a), at the waiting location, an angle made by astraight line of the surface of the pad 63 and the traveling directionof the sheet S is approximately 55 degrees.

In FIG. 11(b), the solenoid 65 is driven and the stopping members 63 and66 are thus moved to the pressing location as indicated by a dottedline. That is, the sheet S is being pressed onto the inner surface ofthe lower guide plate 62 by an edge ED1 of the pad 63. Display of thelower guide plate 62 is omitted from FIG. 11.

The edge ED1 is on the farther end from the entry location of the sheetS, of the two edges of the pad 63 that are along the traveling directionof the sheet S. The edge ED1 touches the sheet S because the sum of thethickness a of the pad 63 and length c from the end surface (bottom)touching the sheet S of the pad fixing bar 66 to the fulcrum FC isslightly smaller than distance h from the fulcrum FC to the sheet S.

As shown in FIG. 11(b), at the pressing location, an angle made by astraight line of the surface of the pad 63 and the traveling directionof the sheet S is approximately 76 degrees. Difference between angles atthe waiting location and the pressing location is approximately 20degrees.

The stopping members 63 and 66 move from the waiting location to thepressing location by rotating approximately 20 degrees in the samedirection as the traveling direction of the sheet S, and return from thepressing location to the waiting location by rotating approximately 20degrees in the opposite direction to the traveling direction of thesheet S.

Length b of the pad 63 is shorter than length d of the end surface ofthe pad fixing bar 66. The pad 63 is provided near an end of the padfixing bar 66 to which the sheet S enters first. Therefore, an edge ED2(edge of the pressing member attachment), which is on the opposite sideto the sheet S entry side of the end surface of the pad 63, is notcovered by the pad 63. Therefore, the stopping members 63 and 66 ofFIGS. 10, 11(a) and 11(b) have the two edges ED1 and ED2.

At the waiting location, neither of the two edges ED1 or ED2 is touchingthe sheet S (pressing against it). At the pressing location, the edgeED1 is touching the sheet S but the edge ED2 is not.

If both of the two edges ED1 or ED2 at the pressing location aretouching the sheet S, as in FIG. 12(a), and if the pad 63 is worn down,the edge ED2 of the metal part makes contact with the sheet S first, asin FIG. 12(b), and there is a danger that the sheet S cannot be stopped.There is also a danger of damaging the sheet S.

Therefore, while the edge ED1 is touching the sheet S at the pressinglocation, as shown in FIG. 11(b), even if the pad 63 has been worn downduring the life expectancy of the product or between overhaulprocedures, the thickness a of the pad 63 should be selected such thatthe edge ED2 does not touch the sheet S.

The stopping members 63 and 66 pressing as in FIG. 11(b) bring about thefollowing effects.

1) Since the pad 63 is structured so as to move in a circular manner andthe sheet S is braked by the edge ED1, the sheet may be securely heldand sufficiently decelerated even when the sheet S is thick and movesfast. The pad 63 is pulled in the traveling direction of the sheet S byfrictional force occurring between the sheets S as well as by thedriving force of the solenoid 65, and the pad 63 thereby moves furtherin a circular manner. As a result, since the pad 63 is further stronglypressed against the sheet S, a greater braking force may be obtained.Application of the brake on the edge ED1 allows effective decelerationutilizing the traveling force of the sheet S.2) By providing the stopping members 63 and 66 with the two edges ED1and ED2, the sheet S is not blocked from traveling when returning to theopposite direction to the traveling direction nor is the sheet Sdamaged. While the sheet S travels along the bottom surface (innersurface of the lower guide plate 62) when advancing in the travelingdirection, it travels along the top surface (surface of the pad 63) whenreturning in the opposite direction. As the pad 63 is not between theedges ED1 and ED2 at this time, blockage of traveling of the sheet S isreduced.3) The angle made by the straight line perpendicular to the surface ofthe pad 63 and the traveling direction of the sheet S is made smallerthan 90 degrees at the pressing location, and thus sufficientdeceleration of the sheet S and security of a stable folding locationare possible. If the angle becomes 90 degrees and the entire surface ofthe pad 63 touches the sheet S, a stable folding location cannot besecured. If the angle exceeds 90 degrees, the sheet S cannot be stopped.Contrary to the above effect 1, braking becomes weaker due to thetraveling force of the sheet S.

FIG. 11(c) illustrates an example where the length b of the pad 63 isthe same as the length d of the end surface of the pad fixing bar 66.There is no edge ED2 in this example. The working example of FIG. 11(c)does not bring about the above-given effect 2, but does lead to theeffects 1 and 3.

A control system of the device according to the embodiment of thepresent invention will be described while referencing FIG. 13.

CONT denotes a control unit for controlling the solenoids 65 a and 65 band the motor 17 based on signals from an operation panel PAN and aplurality of sensors. The control unit CONT includes a CPU, ROM, RAM,and I/O ports. Controlling is carried out by the CPU executing a programstored in the ROM.

A signal for instructing a folding method for a sheet S, for example, istransmitted from the operation panel PAN. Folding methods will bedescribed while referencing FIG. 20 and the description thereof.

Sensors connected to the control unit CON are given below.

A sheet size sensor SS is for detecting the size of a sheet S placed onthe sheet stocker 2. Detected sizes are A4, A3, etc. The sheet sizesensor SS is well known to those skilled in the art and thereforedetailed description thereof is omitted.

Note that the size of the sheet S may be input from the operation panelPAN instead of using the sheet size sensor SS. There are cases whenprovision of the sheet size sensor SS is unnecessary.

A paper feed sensor FS is for detecting that the sheet S has been loadedonto the sheet transportation means 10 to 16. The paper feed sensor FSis an optical sensor (photointerrupter or the like), for example, and isprovided near the separating plate 3 or the feed roller 10, for example.

Sheet entry sensors 7 a and 7 b are for detecting entry of the sheet Sto the sheet deceleration means 6 a and 6 b, respectively. An example ofinstallation locations is given in FIG. 8.

A paper ejection sensor ES is for detecting ejection of a folded sheetS. The paper ejection sensor ES is provided at the exit E.

A rotary encoder RE is a sensor for detecting the amount of rotation ofthe driving roller 11. A rotating shaft of the rotary encoder RE isconnected to the rotating shaft of the driving roller 11 directly or viaa transmission mechanism such as a gear or the like. When the drivingroller 11 is rotated, the rotary encoder RE outputs a pulse incompliance with the rotation angle. For example, the driving roller 11outputs a single pulse for every Δθ rotation. Counting the number ofpulses may give the rotation angle of the driving roller 11. Thedistance moved by the sheet S may also be known based on the number ofpulses.

Control of the stopping members 63 and 66 will be described whilereferencing FIG. 14. FIG. 14 illustrates a control system of the sheetdeceleration means 6 a or the control system of the sheet decelerationmeans 6 b. Content of controlling both means is almost the same, andthus the sheet deceleration means 6 a and 6 b are not differentiated norare ‘a’ and ‘b’ notated in the following description.

The control system of FIG. 14 is implemented by the CPU executing aprogram. The control system may also be implemented by hardware such asan IC.

Reference numeral 100 denotes a solenoid on-signal generator, whichcontrols so as to start driving the solenoid 65 at a time (t1 in FIG.15) after a predetermined period of time (T1 in FIG. 15 or pulse numberPN1, or otherwise a corrected pulse number PN1′ when correctiondescribed later has been performed) has elapsed from a time (t0 in FIG.15) when entry of the sheet S (end of the sheet S) is detected by thesheet entry sensor 7.

Reference numeral 101 denotes a solenoid driving time setting part,which sets a period of time (T2 in FIG. 15) that the solenoid 65 isdriven and controls so as to stop driving the solenoid 65 at a time (t2in FIG. 15) after this period of time has elapsed.

Reference numeral 102 denotes a velocity calculation unit, whichcalculates the driving velocity of the motor 17 based on driveinformation (e.g., electric current) of the motor 17. For example, whendriving currents are I0, I1 and I2, it can be known in advance that thedriving velocities are v0, v1 and v2 respectively, thereby allowingcalculation of the velocity utilizing this information.

SW denotes a switch for turning on and off a current flowing from apower source PS to the solenoid 65. The switch SW turns on according toan output of the solenoid on-signal generator 100 and turns offaccording to an output of the solenoid driving time setting part 101.

The solenoid on-signal generator 100 includes a solenoid on-locationsetting part (drive starting information setting part) 1001, which setsa drive starting time for the solenoid (stopping member driving part)65, which drives the stopping members 63 and 66, based on an instructionon folding method for a sheet S from the operation panel PAN and anoutput from the sheet size sensor SS, a counter 1002, which startscounting output pulses from the rotary encoder RE when the sheet entrysensor 7 has detected the sheet S, a comparator 1003, which compares thecounter 1002 to output from the solenoid on-location setting part 1001and outputs an on signal to the switch SW when they coincide, and acorrector (correction table) 1004, which stores an adjustment timespecified in accordance with the driving velocity of the motor (sheettransportation means driving part) 17.

The solenoid on-location setting part 1001 establishes a foldinglocation based on aspects of the folding method (twofold, threefold,etc.) and size (A3, A4, etc.) of the sheet S. Since the procedure ofestablishing a folding location is well known to those skilled in theart, description thereof is omitted. The folding location which is theoutput of the solenoid on-location setting part 1001 is expressed as theoutput pulse number PN1 (the corrected pulse number PN1′ when correctionhas been performed) of the rotary encoder RE.

The counter counts the number of output pulses from time t0 and onward.The comparator 1003 turns on the solenoid 65 when the counted number ofpulses becomes PN1 (or PN1′). The time T1 corresponds to time requiredfor the rotary encoder RE to output PN1 (or PN1′) number of pulses.While the location (corresponds to PN1 or PN1′) of the sheet S, which isbraked by the stopping members 63 and 66, does not change, the period oftime T1 changes depending on the rotating speed of the motor 17. Thesolenoid on-location setting part 1001 may be interpreted as settingtimes for turning on the solenoid 65 in accordance with the foldinglocation.

Meanwhile, there is a predetermined time delay ΔT from when the solenoid65 is turned on to when a brake force is applied by the stopping members63 and 66. The corrector (correction table) 1004 performs correction forremoving adverse effects of ΔT. For example, it has the correction tablegiven in FIG. 16, and corrects the value of PN1 in accordance with thedriving velocity of the motor 17 to PN1′. In the example of FIG. 16, λ1is subtracted from PN1 when the driving velocity equals a firstvelocity. Namely, PN1′=PN1−λ1. This corresponds to the actual period oftime from sheet detection to sheet stopping in the case of correctionresulting in PN1′. This correction may be performed by the solenoidon-location setting part 1001. Alternatively, it may be added to theoutput of the counter 1002. The same holds for λ2 and λ3.

The folding location (pulse number PN1) does not change due to thedriving velocity of the motor 17, as described above; however, thecorrector 1004 is necessary since the number of pulses generated at thetime delay ΔT changes. The corrector 1004 may be interpreted asadjusting times for turning on the solenoid 65 using the adjusted valuesλ1, λ2 and λ3.

The adjusted values are established based on the time ΔT required formoving from the waiting location to the pressing location. The greaterthe driving velocity of the motor 17, the greater the absolute values ofthe adjusted values. In other words, the higher the driving velocity ofthe motor 17, the more t1 approaches t0 by correction. Supposing delayof the first velocity is ΔT1, the number of pulses output by the rotaryencoder RE corresponds to the adjusted value (the corrected value) λ1.

The solenoid driving time setting part 101 has a table as given in FIG.17, for example. According to this drawing, when the sheet S is a firstsize and the driving velocity of the motor is a first velocity, time T2,which denotes the duration of the solenoid 65 being on, is

In FIG. 17, the greater the transporting velocity of the sheet S, thelonger the driving time τ, and the larger the size (mass) of the sheetS, the longer the driving time τ. When size increases in order from thefirst size to fourth size and velocity increases in order from the firstvelocity to third velocity, relationships: τ11<τ12<τ13<τ14 and τ11<τ21<τ31 hold true.

Note that even if the mass of the sheet S is different, the driving timeof the solenoid 65 may be not changed. In this case, τ11=τ12=τ13=τ14.

The stopping members 63 and 66 are for decelerating a sheet S, bendingthe sheet S, and folding the bent place using the folding means (thedriving roller 11 and the follower roller 13). In order to achieve thisaim, the stopping members 63 and 66 need to sufficiently decelerate thesheet S. Time necessary for deceleration is expressed as a function ofsize (mass) of the sheet S and travel speed thereof. Since kineticenergy of the sheet S is proportional to the mass and also proportionalto the square of the travel speed, the driving time τin the table ofFIG. 17 is established such that the longer the time, the greater thetransporting velocity of the sheet S, and the longer the time, thelarger the size of the sheet S.

Note that when the driving time τ becomes too long, the sheet S isblocked from moving to the folding means. It is desirable that thedriving time τ is long enough to achieve the above-given aim and bendthe sheet S, and short enough such that it does not block the sheet Sfrom moving to the folding means.

The solenoid on-signal generator 100 sets a drive start time based onthe output of the paper feed sensor FS instead of the sheet entry sensor7 when the size of the sheet S is smaller than a predeterminedthreshold. The processing flowchart is given in FIG. 18.

When the sheet S is small, merely driving the stopping members 63 and 66based on the output from the sheet entry sensor 7 may not be enough.This is when T1 in FIG. 15 is shorter than or approximately the same asthe time delay ΔT. At this time, if the driving start time is set basedon the output of the paper feeder sensor FS, T1 can be made sufficientlylong, and thus the stopping members 63 and 66 may make contact at anappropriate location.

The aforementioned threshold is established based on the relationshipbetween T1 and ΔT, for example. For example, when the corrected resultfrom the corrector 1004 is zero or smaller than a predetermined value(value with an allowance for heightening reliability), the output of thepaper feeder sensor FS is used.

Operation of the sheet folding device including the sheet decelerationmeans 6 a and 6 b configured as described above will be described.

FIG. 19 illustrates that the pad 63 of both of the sheet decelerationmeans 6 a and 6 b is at the pressing location; however, in actuality,they are at either the waiting location or the pressing locationdepending on the situation, as described below.

In FIG. 19, the sheet S first passes between the driving roller 11 andthe follower roller 12 and is fed into the gap G of the sheetdeceleration means 6 a located above them.

At this time, the pad 63 is at the waiting location and allows entry ofthe sheet S into the gap G.

When the sheet S is detected by the sheet entry sensor 7, the solenoid65 is driven based on that detection signal, thereby moving the pad 63to the pressing location.

The sheet S is pressed onto the inner surface of the gap G by the pad63. The sheet S is then sandwiched between the pad 63 and the lowerguide plate 62 and stopped from traveling.

The back end side of the sheet S is between the driving roller 11 andthe follower roller 12 and is continued to be sent forward (downstream)from these rollers 11 and 12. The sheet S is bent downward between thedriving roller 11 and the pad 63. The bent portion Sa is caught betweenthe driving roller 11 and the follower roller 13.

The bent portion Sa of the sheet S is folded by the driving roller 11and the follower roller 13, and the sheet S with the bent portion as thefront end is fed into the gap G of the sheet deceleration means 6 blocated below.

In the same manner as with the sheet deceleration means 6 a, the sheet Sis bent and the bent portion Sb is caught between the driving roller 11and the follower roller 14.

The sheet S that has passed between the driving roller 11 and thefollower roller 14 is ejected to the outside through the conveyance path19.

The sheet folding device according to the embodiment of the presentinvention allows various folding methods illustrated in FIG. 20. FIG.20(a) illustrates an outer threefold method, FIG. 20(b) illustrates aninner threefold method, and FIG. 20(c) illustrates a fourfold method.

A shutter device, omitted from the drawing, adjacent to either one ofthe sheet deceleration means 6 a and 6 b may be provided so as toprohibit entry of the sheet S into the gap G such that the sheet S isdecelerated only by the other sheet decelerating means, thereby foldingthe sheet in two as shown in FIG. 20(d).

Which folding method of FIG. 20 is used depends on the operating timingof the pad 63. The operating timing is set by the solenoid on-signalgenerator 100.

The present invention is not limited to the configuration given above.Alternatively, for example, the pad 63 and its transfer means 64 may beprovided on the bottom side of the lower guide plate 62 such that thesheet S that has entered into the gap G will be pressed against thebottom (inner surface) of the upper guide plate 61 by the pad 63.

The paired upper and lower guide members forming the gap G are notlimited to plate materials such as the upper guide plate 61 and thelower guide plate 62. The guide members may be configured by stackingand arranging in parallel a plurality of bars.

As shown in FIG. 8 and FIG. 9, the pivots 68 and 68 for the pad fixingbar 66 are held freely pivoting by the brackets 61 b and 61 b of theupper guide plate 61, respectively. The brackets 61 b and 61 b areintegrally configured with the upper guide plate 61 as one body, andtherefore, the pad fixing bar 66 has a fixed positional relationshipwith the upper guide plate 61 and the lower guide plate 62 withoutmoving except for rotating on the pivots 68 and 68. That is, theposition of the pad fixing bar 66 is fixed. This can also be said aboutthe relationship with the sheet S passing therebetween.

As shown in FIG. 11, the pad 63 displays a braking force by makingcontact with the sheet S so as to stop the sheet S. Contact between thepad 63 and the sheet S favorably occurs along the length (perpendicularto the travelling direction of the sheet S and perpendicular to FIG. 11)of the pad 63 at the same time and degree. In other words, it isfavorable that the state shown in FIG. 11(b) occurs simultaneously atany arbitrary point on the pad 63.

Even if the above conditions are not satisfied, such as one end of thepad 63 is in contact with the sheet S but the other end has not madecontact yet, the sheet S is stopped on said one end while the sheet isnot stopped sufficiently on said other end, and could still be moving.This means that the sheet moves at an angle, that is, oblique motionoccurs. As a result, a phenomenon that endpoints of the folded sheet Sdo not match occurs. This leads to decrease in quality of sheet folding.This is not a favorable phenomenon and should be improved.

In order to satisfy the above conditions, the pad fixing bar 66 shouldbe accurately attached in parallel to the upper guide plate 61 and thelower guide plate 62. However, a slight error occurs due to insufficientmachining precision. Moreover, the above conditions are also notsatisfied when the pad 63 is worn down nonuniformly due to use over along period of time. If the above conditions are not satisfied even alittle, the above problematic phenomenon occurs. The above problematicphenomenon occurs even if, for example, difference between the distancefrom the pivot 68 on one end of the pad fixing bar 66 to the lower guideplate 62 and distance from the pivot 68 on the other end to the same isapproximately 0.5 mm.

FIG. 21 to FIG. 24 show a deceleration means 6 including a mechanismthat can satisfy the above conditions and keep the above problematicphenomenon from occurring. This deceleration means 6 makes contactbetween the pad 63 and the sheet S along the length thereof occur at thesame time and degree.

FIG. 21 is a planar view of the deceleration means 6 according to amodification; FIG. 22 is a front view of the same; FIG. 23 is a rightside view of the same; and FIG. 24 is an exploded view of the same.

In these drawings, the same reference numerals are given to the same orequivalent elements shown in FIG. 7 to FIG. 10, and description thereofis omitted.

CA denotes a seesaw fulcrum (the rotating shaft of the pad fixing bar66).

Reference numeral 161 denotes a pad fixing bar holder attached to aseesaw mechanism attachment 61V, which is made by bending the ends ofthe upper guide plate 61 into a right angle. The pad fixing bar holder161 includes side surfaces 161 b and 161 b parallel to each other, eachprovided with a hole 161 h for the pivot 68, and a base 161 c facing theseesaw mechanism attachment 61V while supporting the side surfaces. Inthe example of this drawing, the pad fixing bar holder 161 is made bybending a plate-like material.

The pad fixing bar holder 161 is attached to the seesaw mechanismattachment 61V by two screws (omitted from the drawing). These screwsare fixed to a mounting plate 162 via collars C2 and C2, respectively.Holes (illustrated in the drawing but without reference numerals) in thebase 161 c for the collars C2 and C2 to pass through are slightly largerthan the collars C2 and C2, thus allowing the pad fixing bar holder 161to move a little against the seesaw mechanism attachment 61V.

Sufficiently large holes (illustrated in the drawing but withoutreference numerals) for a transmission link 67 and an extension rod 65 ato pass through are opened at nearly the center of the base 161 c andthe seesaw mechanism attachment 61V, respectively. A collar 163 passesthrough this hole in the base 161 c so as to be inserted in the hole ofthe seesaw mechanism attachment 61V. The collar 163 is pressed by themounting plate 162 and therefore does not come out. The collar 163 alsohas a large enough hole for the transmission link 67 and the extensionrod 65 a to pass through. The collar 163 allows the pad fixing barholder 161 to rotate. Rotation is centered around the transmission link67 and the extension rod 65 a, that is, the drive shaft of the solenoid65.

As a result, the pad fixing bar 66 is supported by a fulcrum CA at apredetermined position thereof (e.g., center), and is thus capable ofmoving around this fulcrum CA. The rotating shaft is parallel to thetravelling direction of the sheet S. In the above example, the rotatingshaft is the drive shaft of the solenoid 65. A mere minimal rotatablerange is sufficient, such as, for example, approximately 0.5 mm at theends of the pad fixing bar 66.

In the above example, friction adding means 164 and 164 are provided onthe outer sides of the collars C2 and C2, respectively. Each of thefriction adding means 164 includes a screw 164 a, a coil spring 164 b,and a washer 164 c. The seesaw mechanism attachment 61V has holes(illustrated in the drawing but without reference numerals) larger thanthe screws 164 a, and via these holes, the screws 164 a are fixed toscrew holes (illustrated in the drawing but without reference numerals)of the base 161 c. While the friction adding means 164 do not preventthe pad fixing bar holder 161 from moving, the pad fixing bar holder 161does not move easily due to frictional force occurring between thewashers 164 c and the seesaw mechanism attachment 61V. This frictionalforce may be adjusted by turning the screws 164 a. The friction addingmeans 164 are for keeping the pad fixing bar 66 from freely movingaround. The friction adding means 164 drive the solenoid 65 to make thesheet S touch the pad 63, thereby adding a predetermined load F on thesheet S such that the pad fixing bar 66 rotates for the first time whenreaction thereto exceeds the frictional force. A minimal required forcefor moving the pad fixing bar 66 is set as threshold Fth. The thresholdFth corresponds to the frictional force and can be adjusted by thescrews 164 a.

The friction adding means 164 may be provided on the side surfaces 161b, respectively.

The friction adding means 164 may apply friction to the collar 163. Forexample, one or more brakeshoes making contact with the side surface ofthe collar 163 may be provided so as to adjust contact pressure thereof.

The friction adding means 164 may also put a sponge or resin, etc. indirect contact with the pad fixing bar holder 161.

The friction adding means 164 may also use electromagnetic force ratherthan mechanical force. For example, a permanent magnet or anelectromagnet is provided to the pad fixing bar holder 161, a permanentmagnet or an electromagnet is provided to the upper guide plate 61 orthe lower guide plate 62, and the suction force and the repulsive forcetherebetween is used so as to adjust the mobility of the pad fixing bar66.

FIG. 25 is an operational schematic diagram of the above example. Thisdrawing is a front view of the pad fixing bar 66 viewed in thetravelling direction of the sheet S. Movement of the pad fixing bar 66viewed from the side is the same as in FIG. 11.

CA denotes a rotating shaft/fulcrum. In this example, it is a driveshaft of the solenoid 65.

The pad fixing bar 66 moves as a seesaw with CA as the fulcrum. Thismakes distance between the pad 63 and the sheet S the same at allpoints. As a result, contact between the pad 63 and the sheet S alongthe length thereof occurs at the same time and degree. The action of thefriction adding means 164 makes the pad fixing bar 66 move when a load Fequal to or greater than the threshold Fth is applied. Even if anoperator carelessly touches the pad fixing bar 66 or the pad fixing barholder 161 when opening the cover so as to expose the deceleration means6 for maintenance, it will not move as long as the force at this time issmaller than the threshold Fth.

The threshold Fth is 1000 gf to 1500 gf, for example. Fluctuation indegree of skew occurs if the threshold Fth is too small, and too muchtime is necessary for the seesaw motion to finish if it is too large.Therefore, many sheets S are consumed until the above conditions arefulfilled. It is favorable to set the threshold Fth so as to satisfy theconditions of controlling skew and making the number of sheets consumedless than a predetermined number until the seesaw motion is finished.

The load F applied to the sheets S from the pad 63 is not uniform mainlydue to speed, weight, and ream weight of the sheets S. Force making thesheet S stand still is thought to be mainly due to force generated fromthe pad 63 receiving traveling force of the sheet S (same effect as thatmade by a wedge). This force changes with time. Note that the load F andthe strength of the solenoid 65 do not have much relevance to eachother. The role of the solenoid 65 is to adhere the pad 63 to the sheetS, and the sheet S will not stand still only by the force of thesolenoid 65.

When there is a plurality of sheet feeding speeds of the sheet foldingdevice to select from, the threshold Fth should be set so as to satisfythe above conditions at the slowest speed, and thus at a speed (slowest)with the smallest load F. If the seesaw mechanism acts even when theload is small, it acts adequately even when the load is large, andcontact between the pad 63 and the sheet S along the length thereofoccurs at the same time and degree. Since the effect of reduction inskew by the seesaw mechanism increases as the load F is increased, theeffect of reduction in skew at other speeds can also be achieved as longas it is made that the effect of reduction in skew even at the slowestspeed is achieved.

FIG. 26 gives the observation results of the deceleration means 6 ofFIG. 21 to FIG. 24. This drawing gives the measurement results of a caseof raising the left end of the pad fixing bar 66 of the sheetdeceleration means 6 a on the upper side, as viewed from the frontthereof, by 0.5 mm, and a case of raising the right end of the same by0.5 mm. However, this 0.5 mm is an offset quantity, where 0 mm indicatesa state of distance between the pad 63 and the sheet S being the same atall points.

The horizontal axis of FIG. 26 gives folding times (the number ofsheets). This chart illustrates an example of folding twenty sheets S.The vertical axis gives the degree of skew (units of mm), whichcorresponds to x in FIG. 27. The solid line in FIG. 27 indicates a sheetS without any skew, and the dotted line indicates a sheet S to whichskew has occurred. The right side is positive and the left side isnegative in the travelling direction of the sheet S.

As is evident from FIG. 26, the degree of skew for five sheets or moreis 0.5 mm or less, which is stable.

According to the deceleration means 6 of FIG. 21 to FIG. 24, contactbetween the pad 63 and the sheet S is automatically adjusted such thatit occurs along the length of the pad 63 at the same time and degree.Skew does not occur or is miniscule, and thus reduction in quality ofsheet folding does not occur.

The deceleration means 6 of FIG. 21 to FIG. 24 allows provision ofexcellent quality sheet folding and absorption of dimensional errorgenerating in the manufacturing process and aged deterioration.

DESCRIPTION OF REFERENCE NUMERALS

-   6 a, 6 b: sheet deceleration means-   7, 7 a, 7 b: sheet entry sensor-   11: driving roller (sheet transportation means, sheet folding means)-   12: follower roller (sheet transportation means)-   13: follower roller (sheet transportation means, sheet folding    means)-   14: follower roller (sheet transportation means, sheet folding    means)-   17: motor (sheet transportation means driving part)-   61: upper guide plate-   62: lower guide plate (guide member)-   63: pad (pressing member, stopping member)-   64: pad transfer means-   65: solenoid (stopping member driving part)-   66: pad fixing bar (pressing member attachment, stopping member)-   161: pad fixing bar holder-   163: collar-   164: friction adding means-   100: solenoid on-signal generator-   1001: solenoid on-location setting part (drive starting information    setting part)-   1002: counter-   1003: comparator-   1004: corrector-   101: solenoid driving time setting part (driving time setting part)-   CA: rotating shaft/fulcrum-   CONT: controlling unit-   ES: paper ejection sensor-   FS: paper feed sensor-   G: gap-   PS: power supply-   RE: rotary encoder-   S: sheet-   SS: sheet size sensor-   SW: switch

1. A sheet folding device comprising: sheet transportation means fortransporting a sheet along a predetermined route; sheet decelerationmeans for decelerating at least a part of the sheet while beingtransported by the sheet transportation means; folding means for foldinga part of the sheet that is bent as the result of deceleration by thesheet deceleration means; and a control unit for controlling the sheetdeceleration means; wherein the sheet deceleration means comprises aguide member for receiving the sheet while the sheet is beingtransported by the sheet transportation means; a stopping member thatcomprises: a plate-like pressing member having a predetermined thicknessand a pressing member attachment having the pressing member on an endsurface facing the sheet and is rotatably held at a predeterminedfulcrum, wherein an edge of the pressing member presses the sheettraveling along the guide member against the guide member; and astopping member driving part for rotating the stopping member around thefulcrum; wherein the stopping member is positioned at a waiting locationwhere the pressing member does not touch the sheet or at a pressinglocation where the edge of the pressing member touches the sheet but theentire surface of the pressing member does not touch the sheet; thestopping member moves from the waiting location to the pressing locationby rotating in the same direction as the traveling direction of thesheet, and returns from the pressing location to the waiting location byrotating in the opposite direction to the traveling direction of thesheet; the stopping member driving part rotates the stopping member fromthe waiting location to the pressing location in compliance with aninstruction from the control unit; the stopping member is held so as torotate along a parallel axis to the travelling direction of the sheet;and the stopping member rotates due to a reaction to the sheet beingpressed against the guide member by an edge of the stopping member. 2.The sheet folding device of claim 1, further comprising friction addingmeans for adding a predetermined frictional force to the stopping membersuch that the stopping member does not rotate due to the reaction thatis smaller than a predetermined threshold Fth.
 3. The sheet foldingdevice of claim 2, wherein the sheet transportation means is fortransporting the sheet at any one of predetermined multiple speeds, andthe threshold Fth is specified such that the stopping member rotates dueto the reaction in the case of transporting the sheet at the slowestspeed of the multiple speeds.